EP1385723B1 - Electropneumatic control valve with a seal arrangement - Google Patents

Electropneumatic control valve with a seal arrangement Download PDF

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Publication number
EP1385723B1
EP1385723B1 EP02745268A EP02745268A EP1385723B1 EP 1385723 B1 EP1385723 B1 EP 1385723B1 EP 02745268 A EP02745268 A EP 02745268A EP 02745268 A EP02745268 A EP 02745268A EP 1385723 B1 EP1385723 B1 EP 1385723B1
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EP
European Patent Office
Prior art keywords
sealing
valve housing
electro
housing
pneumatic regulating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02745268A
Other languages
German (de)
French (fr)
Other versions
EP1385723A2 (en
Inventor
Friedbert Roether
Siegmund Deja
Eberhard Schaffert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH, Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP1385723A2 publication Critical patent/EP1385723A2/en
Application granted granted Critical
Publication of EP1385723B1 publication Critical patent/EP1385723B1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/321—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration deceleration
    • B60T8/3255—Systems in which the braking action is dependent on brake pedal data
    • B60T8/327—Pneumatic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/361—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force wherein the pilot valve is mounted in a circuit controlling an auxiliary fluid system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/362—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in pneumatic systems

Definitions

  • the invention relates to an electropneumatic control valve for a compressed air brake system of a vehicle having a relay valve housing, in which an axially adjustable control piston for actuating a pressure flow between several outer terminals switching valve seat assembly is arranged, wherein the control piston via at least one electromagnetic pilot valve for axial adjustment can be acted upon, which in a pilot valve housing is housed, which is releasably connected via a seal arrangement with the relay valve housing.
  • the present invention is concerned with a specific embodiment of this seal arrangement.
  • An electropneumatic control valve of this type is used within an air brake system of a vehicle to correct a brake pressure according to the desired - predetermined by a currently employed by a tractor-driven - braking effect.
  • a brake line emanating from the control valve is usually connected with a brake cylinder for this purpose, which in turn generates the braking force required to brake the vehicle and transmits it to a disk or drum brake connected to the piston rod side.
  • the specification of the desired pressure value for the electropneumatic control valve can be carried out both electrically and pneumatically. However, the pneumatic control is usually only used for safety in case of failure of the electrical control.
  • a generic electro-pneumatic control valve is from the DE 196 05 562 A1 known.
  • the control valve for a compressed air brake system of a commercial vehicle has a two-part metallic housing.
  • the lower relay valve body has a brake line port, a boost port, and a bleed port.
  • an inner valve seat arrangement consisting of a closure element which presses against two concentric valve seats, a compressed air flow can be switched between the outer connections.
  • the closure element is actuated axially against the force of a return spring.
  • the actuation of the closure element via a likewise in the relay valve housing arranged within a cavity large-scale control piston.
  • the control piston is acted upon by a control pressure for longitudinal adjustment, wherein the control pressure is generated via a pilot valve arrangement.
  • the pilot valve assembly is disposed within a pilot valve housing mounted on the relay valve housing.
  • the one solenoid valve is normally closed and communicates via gepatiuseinteme pressure fluid channels with the feed pressure port.
  • the working port of the solenoid valve is connected to the control chamber.
  • the second solenoid valve is used to vent the control chamber and is normally closed.
  • the solenoid valve is also connected to the working chamber side with the control chamber, whereas the solenoid valve is connected to the exhaust air side with the atmosphere.
  • the control pressure is changed by a coordinated energizing of both solenoid valves. This change is made according to a pressure control.
  • a pressure sensor is arranged in a working chamber of the control valve.
  • an electronic control system is provided, to which the two solenoid valves and the pressure sensor are connected.
  • the setpoint specification for the control is provided by a remote central control unit of the compressed air brake system.
  • the two housing halves are connected to each other via a sealing ring to prevent leakage of compressed air from the adjacently arranged to the control chamber working chamber of the control valve.
  • a sealing ring is used which is inserted in mutually corresponding paragraph-like recesses between the two housing halves.
  • another sealing ring is held within an outer radial groove-shaped recess on the control piston for dynamic control piston seal. This sealing ring slides in an axial adjustment the control piston sealing along the wall of the control / working chamber of the control valve.
  • a disadvantage of this seal arrangement is the fact that corresponding groove-shaped recesses or shoulders must be produced at the components which receive the sealing rings described above. This is usually only by an additional operation - usually by cutting - possible. Furthermore, it is also necessary to seal valve-internal pressure medium channels, which run between the relay valve housing and the pilot valve housing, via separate individual sealing rings in the connection region of the two housing parts. All the aforementioned sealing elements are expensive to assemble, since the assembly can not be automated. In manual assembly occasionally individual sealing elements are forgotten, resulting in a high reworking effort.
  • a seal arrangement between the relay valve housing and the pilot valve housing is formed as a substantially annular combination seal member having an outer radial seal portion for static housing seal and an inner radial seal portion for dynamic control piston seal.
  • the advantage of the sealing arrangement according to the invention lies in a production and assembly cost-reducing functional integration.
  • the dynamic spool seal is displaced from placement within a groove on the spool to placement by the valve housing.
  • the placement on the part of the valve housing takes place with the inclusion of the static housing seal between the two housing parts.
  • the assembly is easier and faster to accomplish. It is no longer necessary to attach a groove-shaped recess for receiving a sealing ring on the control piston, which reduces the production cost for the control piston.
  • the inner radial sealing portion on the control piston is formed in the manner of a double lip seal.
  • the two elastic sealing lips of the double lip seal spread apart leg-like and substantially axially aligned from the radially extending seal main section.
  • This two-sided lip seal helps to reduce friction in the dynamic spool seal.
  • the contact with the sealing partner, here the control piston takes place only via two axially spaced circumferential sealing lines. Due to the concomitant friction reduction even a smaller piston effective diameter can be selected due to the favorable balance of forces.
  • the other, radially sealing between the relay valve housing and the pilot valve housing outer radial sealing portion of the combination seal member may be formed as an integrally formed on the radially extending seal main portion elastic sealing bead.
  • the sealing bead is preferably formed triangular in cross-section and runs to a sealing edge, which corresponds to the sealing partner - here the relay valve housing on the one hand and the pilot valve housing on the other. This sealing contour allows reliable static sealing of both housing parts, so that an outflow is prevented by pressure medium from the inside of the control valve to the atmosphere.
  • an opening can be made in the region of the sealing main section at at least one point on the circumference of the annular combination sealing element.
  • the at least one breakthrough allows connection of a valve internal pressure medium passage extending from the relay valve housing to the pilot valve housing.
  • the opening is preferably surrounded on both sides with a sealing bead.
  • a pressure compensation element can likewise be placed at at least one point on the circumference of the annular combination sealing element.
  • the pressure compensation element allows a protected pressure equalization with the atmosphere for areas within the pilot valve housing, which are not formed as a pressure chamber, such as the electronics compartment.
  • the pressure compensation element is preferably vulcanized into the combination sealing element during manufacture or subsequently buttoned.
  • the electropneumatic control valve shown has a two-part housing consisting of a lower relay valve housing 1, which is connected to an upper pilot valve housing 2 via an intermediate combination sealing element 3. The connection is made via a (not shown) screw.
  • the relay valve housing 1 and the pilot valve housing 2 include an internal control chamber 4, in which a control piston 5 is arranged axially movable.
  • a control piston 5 is arranged axially movable.
  • the pilot valve arrangement is electrically actuated via an electronic unit 7 likewise arranged in the pilot valve housing 2.
  • pilot valve 6 shown vented when actuated the control chamber 4, wherein the exhaust air is discharged via a coaxial vent channel 8 to the atmosphere.
  • a second pilot valve as an inlet valve is present, which serves for acting on the control chamber 4 with a control pressure to actuate the control piston 5.
  • valve seat arrangement 9 consists essentially of a closure element 10 which is pressed against two concentrically arranged adjacent valve seats by the force of a restoring spring 11.
  • a restoring spring 11 By way of this, the compressed air flow between a arranged on the relay valve housing 1 brake pipe connection 12 on the one hand and a (not visible here) feed pressure port, which is nevertheless in communication with an internal feed pressure chamber 13, and a vent port 14 on the other switchable.
  • the vent port 14 is additionally provided with a muffler 15 for noise reduction of the outflowing exhaust air.
  • the electropneumatic control valve is shown here in its closed switching position. Upon actuation of the control chamber 4 with a control pressure and subsequent movement of the control piston 5 in the direction of a lower position is carried out by opening the outer valve seat of the valve seat assembly 9, a compressed air flow, starting from the feed pressure chamber 13 to a working chamber 15, which opens to the brake pipe 12 to As a result, increase the brake pressure.
  • the control piston 5 With a venting of the control chamber 4, the control piston 5 is transferred to an upper position, wherein the inner valve seat of the valve seat assembly 9 is opened, so that starting from the brake pipe 12 compressed air via the working chamber 16 to the vent port 14 to lower the brake pressure accordingly.
  • the brake pressure is influenced by a reciprocal movement of the control piston 5. There is no compressed air flow in the middle, closed switching position.
  • FIG. 2 shows, arranged between the relay valve housing 1 and the pilot valve housing 2 combination gasket 3 an outer radial sealing portion 17 for static housing sealing and an inner radial sealing portion 18 for dynamic sealing against the control piston 5.
  • the inner radial sealing section 18, which comes to bear dynamically close to the control piston 5, is shaped in the manner of a double lip seal and insofar consists of two elastic sealing lips 19 a, 19b, which spread apart in a leg-like manner substantially axially with respect to a radially extending sealing main section 20.
  • the combination sealing element 3 is formed substantially circular, wherein at several points of the seal main portion 20 various openings 21 a, 21 b, 21 c are provided.
  • the openings 21 a-21 c are used to connect extending between the relay valve housing and the pilot valve housing valve-internal pressure medium channels.
  • a pressure compensation element 22 is provided in the region of the seal main section 20.
  • the pressure compensation element 22 is used for internal pressure equalization of the housing and, in this embodiment, is vulcanized into the combination sealing element 3 during its production.
  • a reinforcing insert 23 is provided made of steel.
  • a sealing bead 24 a, 24 b is integrally formed on both sides of the sealing main section 20 in order to reliably seal the valve-internal pressure medium channel in the region of this connection point.
  • FIG. 5 the position of the pressure compensation element 22 within the combination sealing element 3 emerges.
  • the pressure compensation element 22 is arranged in the same plane as the adjacent reinforcing insert 23.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Electromagnetism (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Fluid-Driven Valves (AREA)
  • Lift Valve (AREA)

Abstract

The invention relates to an electropneumatic control valve for a compressed air braking system on a vehicle, with a relay valve housing (1), in which is arranged an axially displaceable control piston (5), for operating a valve seat arrangement (9), switching the compressed air flow between several external connectors (11, 13). The control piston (5) may be pressurised for axial positioning, by means of at least one electromagnetic pilot valve (6), housed in a pilot valve housing (2), detachably connected to the relay valve housing (1) by means of a seal arrangement, whereby said seal arrangement is embodied as an essentially annular combination seal element (3) between the relay valve housing (1) and the pilot valve housing (2) with a seal section (17) on the external radius for static sealing of the housing and a seal section (18) on the internal radius for dynamic sealing of the control piston.

Description

Die Erfindung betrifft ein elektropneumatisches Regelventil für ein Druckluftbremssystem eines Fahrzeuges mit einem Relaisventilgehäuse, in dem ein axial verstellbarer Steuerkolben zur Betätigung einer den Druckfluss zwischen mehreren äußeren Anschlüssen schaltenden Ventilsitzanordnung angeordnet ist, wobei der Steuerkolben über mindestens ein elektromagnetisches Vorsteuerventil zur Axialverstellung beaufschlagbar ist, welches in einem Vorsteuerventilgehäuse untergebracht ist, das über eine Dichtungsanordnung mit dem Relaisventilgehäuse lösbar verbunden ist. Insbesondere befasst sich die vorliegende Erfindung mit einer speziellen Ausbildung dieser Dichtungsanordnung.The invention relates to an electropneumatic control valve for a compressed air brake system of a vehicle having a relay valve housing, in which an axially adjustable control piston for actuating a pressure flow between several outer terminals switching valve seat assembly is arranged, wherein the control piston via at least one electromagnetic pilot valve for axial adjustment can be acted upon, which in a pilot valve housing is housed, which is releasably connected via a seal arrangement with the relay valve housing. In particular, the present invention is concerned with a specific embodiment of this seal arrangement.

Ein elektropneumatisches Regelventil dieser Art wird innerhalb eines Druckluftbremssystems eines Fahrzeuges eingesetzt, um einen Bremsdruck entsprechend der gewünschten - durch ein Fußbremspedal vorgebbaren - Bremswirkung auszuregeln. Eine vom Regelventil ausgehende Bremsleitung steht zu diesem Zwecke gewöhnlich mit einem Bremszylinder in Verbindung, der wiederum die zum Bremsen des Fahrzeuges benötigte Bremskraft erzeugt und an eine kolbenstangenseitig angeschlossene Scheiben- oder Trommelbremse weiterleitet. Die Vorgabe des Druck-Sollwertes für das elektropneumatische Regelventil kann sowohl elektrisch als auch pneumatisch erfolgen. Die pneumatische Ansteuerung wird meist jedoch nur zur Sicherheit im Falle eines Ausfalls der elektrischen Ansteuerung benutzt.An electropneumatic control valve of this type is used within an air brake system of a vehicle to correct a brake pressure according to the desired - predetermined by a Fußbremspedal - braking effect. A brake line emanating from the control valve is usually connected with a brake cylinder for this purpose, which in turn generates the braking force required to brake the vehicle and transmits it to a disk or drum brake connected to the piston rod side. The specification of the desired pressure value for the electropneumatic control valve can be carried out both electrically and pneumatically. However, the pneumatic control is usually only used for safety in case of failure of the electrical control.

Ein gattungsgemäßes elektropneumatisches Regelventil ist aus der DE 196 05 562 A1 bekannt. Das Regelventil für ein Druckluftbremssystem eines Nutzfahrzeuges weist ein zweigeteiltes metallisches Gehäuse auf. Am unteren Relaisventilgehäuse befinden sich ein Bremsleitungsanschluss, ein Speisedruckanschluss sowie ein Entlüftungsanschluss. Über eine innenliegende Ventilsitzanordnung, bestehend aus einem gegen zwei konzentrische Ventilsitze drückendes Verschlusselement, ist ein Druckluftfluss zwischen den äußeren Anschlüssen schaltbar. Zum Schalten wird das Verschlusselement entgegen der Kraft einer Rückstellfeder axial betätigt. Die Betätigung des Verschlusselementes erfolgt über einen ebenfalls im Relaisventilgehäuse innerhalb eines Hohlraumes angeordneten großflächigen Steuerkolben. Der Steuerkolben wird über einen Steuerdruck zur Längsverstellung beaufschlagt, wobei der Steuerdruck über eine Vorsteuerventilanordnung erzeugt wird. Die Vorsteuerventilanordnung ist innerhalb eines am Relaisventilgehäuse angebrachten Vorsteuerventilgehäuses angeordnet. Zur Einstellung oder Änderung des Steuerdrucks dienen zwei einzelne Elektromagnetventile. Das eine Elektromagnetventil ist stromlos geschlossen und kommuniziert über gehäuseinteme Druckmittelkanäle mit dem Speisedruckanschluss. Der Arbeitsanschluss des Elektromagnetventils ist mit der Steuerkammer verbunden. Das zweite Elektromagnetventil dient dem Entlüften der Steuerkammer und ist stromlos geschlossen. Das Elektromagnetventil ist ebenfalls arbeitsleitungsseitig mit der Steuerkammer verbunden, wogegen das Elektromagnetventil abluftseitig mit der Atmosphäre in Verbindung steht. Der Steuerdruck wird durch ein koordiniertes Bestromen beider Elektromagnetventile verändert. Diese Änderung erfolgt entsprechend einer Druckregelung. Zur Überwachung des Arbeitsdrucks ist ein Drucksensor in einer Arbeitskammer des Regelventils angeordnet. Ferner ist eine Regelelektronik vorgesehen, an welche die beiden Elektromagnetventile sowie der Drucksensor angeschlossen sind. Die Sollwert-Vorgabe für die Regelung erfolgt von einer entfernt angeordneten zentralen Steuereinheit des Druckluftbremssystems.A generic electro-pneumatic control valve is from the DE 196 05 562 A1 known. The control valve for a compressed air brake system of a commercial vehicle has a two-part metallic housing. The lower relay valve body has a brake line port, a boost port, and a bleed port. By means of an inner valve seat arrangement, consisting of a closure element which presses against two concentric valve seats, a compressed air flow can be switched between the outer connections. For switching, the closure element is actuated axially against the force of a return spring. The actuation of the closure element via a likewise in the relay valve housing arranged within a cavity large-scale control piston. The control piston is acted upon by a control pressure for longitudinal adjustment, wherein the control pressure is generated via a pilot valve arrangement. The pilot valve assembly is disposed within a pilot valve housing mounted on the relay valve housing. To set or change the control pressure are two individual solenoid valves. The one solenoid valve is normally closed and communicates via gehäuseinteme pressure fluid channels with the feed pressure port. The working port of the solenoid valve is connected to the control chamber. The second solenoid valve is used to vent the control chamber and is normally closed. The solenoid valve is also connected to the working chamber side with the control chamber, whereas the solenoid valve is connected to the exhaust air side with the atmosphere. The control pressure is changed by a coordinated energizing of both solenoid valves. This change is made according to a pressure control. For monitoring the working pressure, a pressure sensor is arranged in a working chamber of the control valve. Furthermore, an electronic control system is provided, to which the two solenoid valves and the pressure sensor are connected. The setpoint specification for the control is provided by a remote central control unit of the compressed air brake system.

Bei dem vorstehend beschriebenen Regelventil sind eine Reihe von Dichtungsmaßnahmen erforderlich, um eine zuverlässige Trennung von Bereichen unterschiedlichen Drucks sicherzustellen. So werden die beiden Gehäusehälften über einen Dichtring miteinander verbunden, um ein Abströmen von Druckluft aus der benachbart zur Steuerkammer angeordneten Arbeitskammer des Regelventils zu verhindern. Hierfür wird ein Dichtring verwendet, der in miteinander korrespondierenden absatzartigen Ausnehmungen zwischen die beiden Gehäusehälften eingelegt ist. In örtlicher Nähe dieser statischen Gehäuseabdichtung ist zur dynamischen Steuerkolbenabdichtung ein weiterer Dichtring innerhalb einer außenradialen nutförmigen Ausnehmung am Steuerkolben gehalten. Dieser Dichtring gleitet bei einer Axialverstellung des Steuerkolbens dichtend entlang der Wandung der Steuer- /Arbeitskammer des Regelventils.In the control valve described above, a number of sealing measures are required to ensure reliable separation of regions of different pressure. Thus, the two housing halves are connected to each other via a sealing ring to prevent leakage of compressed air from the adjacently arranged to the control chamber working chamber of the control valve. For this purpose, a sealing ring is used which is inserted in mutually corresponding paragraph-like recesses between the two housing halves. In the vicinity of this static housing seal another sealing ring is held within an outer radial groove-shaped recess on the control piston for dynamic control piston seal. This sealing ring slides in an axial adjustment the control piston sealing along the wall of the control / working chamber of the control valve.

Ein Nachteil dieser Dichtungsanordnung ist darin zu sehen, dass an den die vorstehend beschriebenen Dichtringe aufnehmenden Bauteilen entsprechende nutförmige Ausnehmungen oder Absätze hergestellt werden müssen. Dies ist gewöhnlich nur durch einen zusätzlichen Arbeitsgang - meist durch Spanen - möglich. Weiterhin ist es erforderlich, auch ventilinteme Druckmittelkanäle, die zwischen dem Relaisventilgehäuse und dem Vorsteuerventilgehäuse verlaufen, über separate einzelne Dichtringe im Verbindungsbereich beider Gehäuseteile abzudichten. All die vorstehend genannten Dichtelemente sind aufwendig zu montieren, da die Montage nicht automatisierbar ist. Bei der manuellen Montage werden vereinzelt auch einzelne Dichtungselemente vergessen, was zu einem hohen Nacharbeitsaufwand führt.A disadvantage of this seal arrangement is the fact that corresponding groove-shaped recesses or shoulders must be produced at the components which receive the sealing rings described above. This is usually only by an additional operation - usually by cutting - possible. Furthermore, it is also necessary to seal valve-internal pressure medium channels, which run between the relay valve housing and the pilot valve housing, via separate individual sealing rings in the connection region of the two housing parts. All the aforementioned sealing elements are expensive to assemble, since the assembly can not be automated. In manual assembly occasionally individual sealing elements are forgotten, resulting in a high reworking effort.

Es ist daher die Aufgabe der vorliegenden Erfindung, eine Dichtungsanordnung für ein gattungsgemäßes elektromagnetisches Regelventil zu schaffen, die zum einen zu einer Minimierung des Fertigungsaufwandes an den Gehäusebestandteilen führt und die zum anderen auch eine einfache Montage gewährleistet.It is therefore an object of the present invention to provide a seal assembly for a generic electromagnetic control valve, which leads to a minimization of manufacturing costs to the housing components and on the other hand ensures easy installation.

Die Aufgabe wird ausgehend von einem elektropneumatischen Regelventil gemäß dem Oberbegriff des Anspruchs 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of an electropneumatic control valve according to the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give advantageous developments of the invention.

Die Erfindung schließt die technische Lehre ein, dass eine Dichtungsanordnung zwischen dem Relaisventilgehäuse und dem Vorsteuerventilgehäuse als ein im Wesentlichen ringförmiges Kombinationsdichtungselement ausgebildet ist, das einen außenradialen Dichtungsabschnitt zur statischen Gehäuseabdichtung sowie einen innenradialen Dichtungsabschnitt zur dynamischen Steuerkolbenabdichtung aufweist.The invention includes the technical teaching that a seal arrangement between the relay valve housing and the pilot valve housing is formed as a substantially annular combination seal member having an outer radial seal portion for static housing seal and an inner radial seal portion for dynamic control piston seal.

Der Vorteil der erfindungsgemäßen Dichtungsanordnung liegt in einer fertigungs- und montageaufwandreduzierenden Funktionsintegration. Um diese Funktionsintegration zu erzielen, wird bei der Erfindung die dynamische Steuerkolbenabdichtung von einer Platzierung innerhalb einer Nut am Steuerkolben verlagert zu einer Platzierung seitens des Ventilgehäuses. Die Platzierung seitens des Ventilgehäuses erfolgt dabei unter Einbeziehung der statischen Gehäuseabdichtung zwischen den beiden Gehäuseteilen. Da nunmehr weniger einzelne Dichtungen vorhanden sind, ist die Montage einfacher und schneller zu bewerkstelligen. Es ist nicht mehr erforderlich, am Steuerkolben eine nutförmige Ausnehmung zur Aufnahme eines Dichtrings anzubringen, was den Fertigungsaufwand für den Steuerkolben reduziert.The advantage of the sealing arrangement according to the invention lies in a production and assembly cost-reducing functional integration. In order to achieve this functional integration, in the invention, the dynamic spool seal is displaced from placement within a groove on the spool to placement by the valve housing. The placement on the part of the valve housing takes place with the inclusion of the static housing seal between the two housing parts. Now that fewer individual seals are present, the assembly is easier and faster to accomplish. It is no longer necessary to attach a groove-shaped recess for receiving a sealing ring on the control piston, which reduces the production cost for the control piston.

Vorzugsweise ist der am Steuerkolben dynamisch dicht zur Anlage kommende innenradiale Dichtungsabschnitt nach Art einer Doppellippendichtung geformt. Die beiden elastischen Dichtlippen der Doppellippendichtung spreizen sich dabei schenkelartig und im Wesentlichen axial ausgerichtet von dem sich radial erstreckenden Dichtungshauptabschnitt ab. Diese zweiseitige Lippendichtung trägt zu einer Reduzierung der Reibung bei der dynamischen Steuerkolbenabdichtung bei. Der Kontakt zum Dichtungspartner, hier dem Steuerkolben, erfolgt lediglich über zwei axial beabstandete umlaufende Dichtlinien. Durch die damit einhergehende Reibungsreduzierung kann infolge der günstigen Kräftebilanz sogar ein kleinerer Kolbenwirkdurchmesser gewählt werden.Preferably, the inner radial sealing portion on the control piston is formed in the manner of a double lip seal. The two elastic sealing lips of the double lip seal spread apart leg-like and substantially axially aligned from the radially extending seal main section. This two-sided lip seal helps to reduce friction in the dynamic spool seal. The contact with the sealing partner, here the control piston, takes place only via two axially spaced circumferential sealing lines. Due to the concomitant friction reduction even a smaller piston effective diameter can be selected due to the favorable balance of forces.

Der andere, zwischen dem Relaisventilgehäuse und dem Vorsteuerventilgehäuse statisch dichtende außenradiale Dichtungsabschnitt des Kombinationsdichtungselements kann als ein am sich radial erstreckenden Dichtungshauptabschnitt angeformter elastischer Dichtwulst ausgebildet sein. Der Dichtwulst ist vorzugsweise im Querschnitt gesehen dreieckig ausgebildet und läuft zu einer Dichtkante aus, die mit dem Dichtungspartner - hier dem Relaisventilgehäuse einerseits und dem Vorsteuerventilgehäuse andererseits - korrespondiert. Diese Dichtungskontur ermöglicht eine zuverlässige statische Abdichtung beider Gehäuseteile, so dass ein Abströmen von Druckmittel aus dem Inneren des Regelventils an die Atmosphäre verhindert wird.The other, radially sealing between the relay valve housing and the pilot valve housing outer radial sealing portion of the combination seal member may be formed as an integrally formed on the radially extending seal main portion elastic sealing bead. The sealing bead is preferably formed triangular in cross-section and runs to a sealing edge, which corresponds to the sealing partner - here the relay valve housing on the one hand and the pilot valve housing on the other. This sealing contour allows reliable static sealing of both housing parts, so that an outflow is prevented by pressure medium from the inside of the control valve to the atmosphere.

Innerhalb des ebenfalls aus einem elastischen Dichtungsmaterial bestehenden Dichtungshauptabschnittes kann eine innenliegende Verstärkungseinlage - beispielsweise aus Stahl - eingegossen werden, um die Stabilität des Kombinationsdichtungselements zu erhöhen.Within the sealing main section, which likewise consists of an elastic sealing material, an internal reinforcing insert-for example of steel-can be cast in order to increase the stability of the combination sealing element.

Gemäß einer weiteren, die Erfindung verbesserenden Maßnahme kann im Bereich des Dichtungshauptabschnittes an mindestens einer Stelle auf dem Umfang des ringförmigen Kombinationsdichtungselements ein Durchbruch angebracht werden. Der mindestens eine Durchbruch gestattet eine Verbindung eines vom Relaisventilgehäuse zum Vorsteuerventilgehäuse verlaufenden ventilinternen Druckmittelkanals. Um auch für einen solchen Druckmittelkanal eine zuverlässige Abdichtung sicherzustellen, ist der Durchbruch vorzugsweise beidseitig mit einer Dichtwulst umrandet. Daneben kann im Bereich des Dichtungshauptabschnittes ebenfalls an mindestens einer Stelle auf dem Umfang des ringförmigen Kombinationsdichtungselements ein Druckausgleichselement platziert sein. Das Druckausgleichselement ermöglicht einen geschützten Druckausgleich mit der Atmosphäre für Bereiche innerhalb des Vorsteuerventilgehäuses, die nicht als Druckkammer ausgebildet sind, wie beispielsweise dem Elektronikraum. Das Druckausgleichselement wird in das Kombinationsdichtungselement vorzugsweise bei der Herstellung einvulkanisiert oder nachträglich eingeknöpft.According to a further measure improving the invention, an opening can be made in the region of the sealing main section at at least one point on the circumference of the annular combination sealing element. The at least one breakthrough allows connection of a valve internal pressure medium passage extending from the relay valve housing to the pilot valve housing. In order to ensure a reliable seal for such a pressure medium channel, the opening is preferably surrounded on both sides with a sealing bead. In addition, in the region of the sealing main section, a pressure compensation element can likewise be placed at at least one point on the circumference of the annular combination sealing element. The pressure compensation element allows a protected pressure equalization with the atmosphere for areas within the pilot valve housing, which are not formed as a pressure chamber, such as the electronics compartment. The pressure compensation element is preferably vulcanized into the combination sealing element during manufacture or subsequently buttoned.

Weitere, die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt:

Figur 1
einen Längsschnitt durch ein elektropneumatisches Regelventil mit einer erfindungsgemäßen Dichtungsanordnung,
Figur 2
einen Längsschnitt als Detail im Bereich des Steuerkolbens von Figur 1,
Figur 3
eine Draufsicht auf das Kombinationsdichtungselement,
Figur 4
einen Querschnitt in der Schnittlinie A-A in Figur 3, und
Figur 5
einen Querschnitt durch ein Kombinationsdichtungselement im Bereich eines hierin integrierten Druckausgleichselements.
Further, measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS. It shows:
FIG. 1
a longitudinal section through an electropneumatic control valve with a seal assembly according to the invention,
FIG. 2
a longitudinal section as a detail in the area of the control piston of FIG. 1 .
FIG. 3
a top view of the combination sealing element,
FIG. 4
a cross section in the section line AA in FIG. 3 , and
FIG. 5
a cross section through a combination sealing element in the region of a pressure compensation element integrated therein.

Das in der Figur 1 dargestellte elektropneumatische Regelventil besitzt ein zweigeteiltes Gehäuse, das aus einem unteren Relaisventilgehäuse 1 besteht, welches mit einem oberen Vorsteuerventilgehäuse 2 über ein dazwischenliegendes Kombinationsdichtungselement 3 verbunden ist. Die Verbindung erfolgt dabei über eine (nicht weiter dargestellte) Verschraubung. Das Relaisventilgehäuse 1 und das Vorsteuerventilgehäuse 2 schließen eine innenliegende Steuerkammer 4 ein, in der ein Steuerkolben 5 axial bewegbar angeordnet ist. Zur axialen Verstellung des Steuerkolbens 5 dient eine im Vorsteuerventilgehäuse 2 untergebrachte Vorsteuerventilanordnung, von der hier lediglich ein als Auslassmagnet dienendes Vorsteuerventil 6 gezeigt ist. Die Vorsteuerventilanordnung wird über eine ebenfalls im Vorsteuerventilgehäuse 2 angeordnete Elektronikeinheit 7 elektrisch angesteuert. Das gezeigte Vorsteuerventil 6 entlüftet bei Betätigung die Steuerkammer 4, wobei die Abluft über einen koaxialen Entlüftungskanal 8 an die Atmosphäre abgeleitet wird. Neben dem als Auslassventil dienenden Vorsteuerventil 6 ist ein (hier nicht gezeigtes) zweites Vorsteuerventil als Einlassventil vorhanden, das für eine Beaufschlagung der Steuerkammer 4 mit einem Steuerdruck dient, um den Steuerkolben 5 zu betätigen.That in the FIG. 1 The electropneumatic control valve shown has a two-part housing consisting of a lower relay valve housing 1, which is connected to an upper pilot valve housing 2 via an intermediate combination sealing element 3. The connection is made via a (not shown) screw. The relay valve housing 1 and the pilot valve housing 2 include an internal control chamber 4, in which a control piston 5 is arranged axially movable. For the axial adjustment of the control piston 5 serves a pilot valve housing 2 accommodated in the pilot valve arrangement, of which only one serving as an outlet solenoid pilot valve 6 is shown. The pilot valve arrangement is electrically actuated via an electronic unit 7 likewise arranged in the pilot valve housing 2. The pilot valve 6 shown vented when actuated the control chamber 4, wherein the exhaust air is discharged via a coaxial vent channel 8 to the atmosphere. In addition to serving as an outlet valve pilot valve 6 is a (not shown here) second pilot valve as an inlet valve is present, which serves for acting on the control chamber 4 with a control pressure to actuate the control piston 5.

Bei einer solchen Beaufschlagung der Steuerkammer 4 betätigt der Steuerkolben 5 über eine untere hülsenartige koaxiale Anformung eine Ventilsitzanordnung 9. Die Ventilsitzanordnung 9 besteht im Wesentlichen aus einem Verschlusselement 10, das durch die Kraft einer rückstellenden Feder 11 gegen zwei konzentrisch angeordnete benachbarte Ventilsitze gedrückt wird. Hierüber ist der Druckluftfluss zwischen einem am Relaisventilgehäuse 1 angeordneten Bremsleitungsanschluss 12 einerseits sowie einem (hier nicht erkennbar) Speisedruckanschluss, der gleichwohl mit einer internen Speisedruckkammer 13 in Verbindung steht, und einem Entlüftungsanschluss 14 andererseits schaltbar. Der Entlüftungsanschluss 14 ist zusätzlich mit einem Schalldämpfer 15 zur Geräuschminderung der ausströmenden Abluft versehen.In such an action on the control chamber 4, the control piston 5 actuates a valve seat arrangement 9 via a lower sleeve-like coaxial projection. The valve seat arrangement 9 consists essentially of a closure element 10 which is pressed against two concentrically arranged adjacent valve seats by the force of a restoring spring 11. By way of this, the compressed air flow between a arranged on the relay valve housing 1 brake pipe connection 12 on the one hand and a (not visible here) feed pressure port, which is nevertheless in communication with an internal feed pressure chamber 13, and a vent port 14 on the other switchable. The vent port 14 is additionally provided with a muffler 15 for noise reduction of the outflowing exhaust air.

Das elektropneumatische Regelventil ist hier in seiner abgeschlossenen Schaltstellung gezeigt. Bei Beaufschlagung der Steuerkammer 4 mit einem Steuerdruck und darauf folgender Bewegung des Steuerkolbens 5 in Richtung einer unteren Position erfolgt durch Öffnen des außenliegenden Ventilsitzes der Ventilsitzanordnung 9 ein Druckluftfluss, ausgehend von der Speisedruckkammer 13 zu einer Arbeitskammer 15, die an den Bremsleitungsanschluss 12 einmündet, um den Bremsdruck infolgedessen zu erhöhen.The electropneumatic control valve is shown here in its closed switching position. Upon actuation of the control chamber 4 with a control pressure and subsequent movement of the control piston 5 in the direction of a lower position is carried out by opening the outer valve seat of the valve seat assembly 9, a compressed air flow, starting from the feed pressure chamber 13 to a working chamber 15, which opens to the brake pipe 12 to As a result, increase the brake pressure.

Bei einer Entlüftung der Steuerkammer 4 wird der Steuerkolben 5 in eine obere Position überführt, wobei der innenliegende Ventilsitz der Ventilsitzanordnung 9 geöffnet wird, so dass ausgehend vom Bremsleitungsanschluss 12 Druckluft über die Arbeitskammer 16 zum Entlüftungsanschluss 14 gelangt, um den Bremsdruck entsprechend abzusenken. Somit wird der Bremsdruck durch eine wechselseitige Bewegung des Steuerkolbens 5 beeinflusst. In der mittleren, abgeschlossenen Schaltposition erfolgt kein Druckluftfluss.With a venting of the control chamber 4, the control piston 5 is transferred to an upper position, wherein the inner valve seat of the valve seat assembly 9 is opened, so that starting from the brake pipe 12 compressed air via the working chamber 16 to the vent port 14 to lower the brake pressure accordingly. Thus, the brake pressure is influenced by a reciprocal movement of the control piston 5. There is no compressed air flow in the middle, closed switching position.

Wie deutlicher aus der Figur 2 hervorgeht, weist das zwischen dem Relaisventilgehäuse 1 und dem Vorsteuerventilgehäuse 2 angeordnete Kombinationsdichtungselement 3 einen außenradialen Dichtungsabschnitt 17 zur statischen Gehäuseabdichtung sowie einen innenradialen Dichtungsabschnitt 18 zur dynamischen Abdichtung gegenüber dem Steuerkolben 5 auf. Der am Steuerkolben 5 dynamisch dicht zur Anlage kommende innenradiale Dichtungsabschnitt 18 ist nach Art einer Doppellippendichtung geformt und besteht insoweit aus zwei elastischen Dichtlippen 19a, 19b, die sich schenkelartig im Wesentlichen axial gegenüber einem sich radial erstreckenden Dichtungshauptabschnitt 20 abspreizen.How clearer from the FIG. 2 shows, arranged between the relay valve housing 1 and the pilot valve housing 2 combination gasket 3 an outer radial sealing portion 17 for static housing sealing and an inner radial sealing portion 18 for dynamic sealing against the control piston 5. The inner radial sealing section 18, which comes to bear dynamically close to the control piston 5, is shaped in the manner of a double lip seal and insofar consists of two elastic sealing lips 19 a, 19b, which spread apart in a leg-like manner substantially axially with respect to a radially extending sealing main section 20.

Gemäß Figur 3 ist das Kombinationsdichtungselement 3 im Wesentlichen kreisringförmig ausgebildet, wobei an mehreren Stellen des Dichtungshauptabschnittes 20 diverse Durchbrüche 21 a, 21 b, 21 c vorgesehen sind. Die Durchbrüche 21 a-21 c dienen der Verbindung von zwischen dem Relaisventilgehäuse und dem Vorsteuerventilgehäuse verlaufenden ventilinternen Druckmittelkanälen. Daneben ist im Bereich des Dichtungshauptabschnittes 20 auch ein Druckausgleichselement 22 vorgesehen. Das Druckausgleichselement 22 dient einem gehäuseinternen Druckausgleich und ist in diesem Ausführungsbeispiel in das Kombinationsdichtungselement 3 bei dessen Herstellung einvulkanisiert.According to FIG. 3 is the combination sealing element 3 is formed substantially circular, wherein at several points of the seal main portion 20 various openings 21 a, 21 b, 21 c are provided. The openings 21 a-21 c are used to connect extending between the relay valve housing and the pilot valve housing valve-internal pressure medium channels. In addition, a pressure compensation element 22 is provided in the region of the seal main section 20. The pressure compensation element 22 is used for internal pressure equalization of the housing and, in this embodiment, is vulcanized into the combination sealing element 3 during its production.

Wie aus der Detailansicht gemäß Figur 4 hervorgeht, ist in dem ansonsten aus einem elastischen Dichtungsmaterial bestehenden Kombinationsdichtungselement 3 eine Verstärkungseinlage 23 aus Stahl vorgesehen. Um den hier exemplarisch dargestellten Durchbruch 21 a herum ist beidseitig des Dichtungshauptabschnittes 20 ein Dichtwulst 24a, 24b angeformt, um den ventilinternen Druckmittelkanal im Bereich dieser Verbindungsstelle zuverlässig abzudichten.As from the detail view according to FIG. 4 is apparent, in the otherwise consisting of an elastic sealing material combination sealing element 3, a reinforcing insert 23 is provided made of steel. Around the breakthrough 21 a shown here by way of example, a sealing bead 24 a, 24 b is integrally formed on both sides of the sealing main section 20 in order to reliably seal the valve-internal pressure medium channel in the region of this connection point.

Aus Figur 5 geht die Lage des Druckausgleichselements 22 innerhalb des Kombinationsdichtungselements 3 hervor. Das Druckausgleichselement 22 ist in derselben Ebene wie die benachbarte Verstärkungseinlage 23 angeordnet.Out FIG. 5 the position of the pressure compensation element 22 within the combination sealing element 3 emerges. The pressure compensation element 22 is arranged in the same plane as the adjacent reinforcing insert 23.

Die vorliegende Erfindung ist nicht beschränkt auf das vorstehende, nur beispielhaft angegebene Ausführungsbeispiel. Es sind vielmehr auch Abwandlungen hiervon denkbar, die in den Schutzbereich der nachfolgenden Ansprüche eingreifen können.The present invention is not limited to the above exemplary embodiment given by way of example only. On the contrary, modifications are conceivable which may interfere with the scope of protection of the following claims.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
RelaisventilgehäuseRelay valve housing
22
VorsteuerventilgehäusePilot valve housing
33
KombinationsdichtungselementCombination sealing element
44
Steuerkammercontrol chamber
55
Steuerkolbenspool
66
Vorsteuerventilpilot valve
77
Elektronikeinheitelectronics unit
88th
Entlüftungskanalvent channel
99
VentilsitzanordnungThe valve seat assembly
1010
Verschlusselementclosure element
1111
Federfeather
1212
BremsleitungsanschlussBrake line connection
1313
Arbeitskammerworking chamber
1414
Entlüftungsanschlussexhaust port
1515
Schalldämpfersilencer
1616
Arbeitskammerworking chamber
1717
Dichtungsabschnittsealing section
1818
Dichtungsabschnittsealing section
1919
Dichtlippesealing lip
2020
DichtungshauptabschnittSeal main section
2121
Durchbruchbreakthrough
2222
DruckausgleichselementPressure compensation element
2323
Verstärkungseinlagereinforcing insert
2424
Dichtwulstsealing bead

Claims (11)

  1. Electro-pneumatic regulating valve for a compressed-air system in a vehicle, comprising a relay valve housing (1) in which an axially adjustable control piston (5) is disposed for actuating a valve seat group (9) switching the flow of compressed air between several external connectors (11, 13), with said control piston (5) being adapted to be operated via at least one electromagnetic pilot valve (6) for axial displacement, which is accommodated in a pilot valve housing (2) that is releasably connected via a sealing means to said relay valve housing (1),
    characterised in that said sealing means is designed as a substantially annular combination sealing element (3) between said relay valve housing (1) and said pilot valve housing (2), which comprises an externally radial sealing section (17) for static sealing of the housing as well as an internally radial sealing section (18) for the dynamic sealing of said control piston.
  2. Electro-pneumatic regulating valve according to Claim 1,
    characterised in that said internally radial sealing section (18), which is caused to bear against said control piston (5) for dynamic sealing, is shaped in the manner of a dual lip seal whose two resilient sealing lips (19a, 19b) spread off from the radially extending main sealing section (20) in the manner of branches and with a substantially axial orientation.
  3. Electro-pneumatic regulating valve according to Claim 1,
    characterised in that said externally radial sealing section (17) for static sealing between said relay valve housing (1) and said pilot valve housing (2) is configured as a resilient sealing bead formed on said radially extending main sealing section (20).
  4. Electro-pneumatic regulating valve according to Claim 3,
    characterised in that said radially extending main sealing section (20), which consists of a resilient material, is provided with an inside reinforcing insert (23) made of a rigid material.
  5. Electro-pneumatic regulating valve according to Claim 4,
    characterised in that said reinforcing insert (23) consists of spring steel.
  6. Electro-pneumatic regulating valve according to Claim 3,
    characterised in that an aperture (21a to 21c) is formed in the region of said main sealing section (20) on at least one site along the periphery of said annular combination sealing element (3) so as to ensure a connection of a pressurised-medium passage internal of the valve, which extends from said relay valve housing (1) to said pilot valve housing (2).
  7. Electro-pneumatic regulating valve according to Claim 6,
    characterised in that said at least one aperture (21a to 21c) is surrounded on both sides by a sealing bead (24a, 24b).
  8. Electro-pneumatic regulating valve according to Claim 6,
    characterised in that said pressurised-medium passage internal of the valve, which extends from said relay valve housing (1) to said pilot valve housing (2) supplies at said at least one pilot valve with feeding pressure.
  9. Electro-pneumatic regulating valve according to any of the preceding Claims,
    characterised in that said sealing bead (21 a to 21 c), when seen in its cross-section, presents a triangular or trapezoidal design and terminates towards a sealing edge corresponding to the sealing partner.
  10. Electro-pneumatic regulating valve according to any of the preceding Claims,
    characterised in that a pressure-equalizing element (22) is placed on at least one site along the periphery of said annular combination sealing element (3), in the zone of said main sealing section (20), so as to create protected pressure equalization with the atmosphere for areas in said pilot valve housing (2), which are not employed as pressure chamber.
  11. Electro-pneumatic regulating valve according to any of the preceding Claims,
    characterised in that said pressure-equalizing element (22) is integrated into said main sealing section (20) of said combination sealing element (3) by vulcanisation or tied into it subsequently.
EP02745268A 2001-04-26 2002-04-26 Electropneumatic control valve with a seal arrangement Expired - Lifetime EP1385723B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10120323A DE10120323C1 (en) 2001-04-26 2001-04-26 Electropneumatic control valve with a sealing arrangement
DE10120323 2001-04-26
PCT/EP2002/004633 WO2002087938A2 (en) 2001-04-26 2002-04-26 Electropneumatic control valve with a seal arrangement

Publications (2)

Publication Number Publication Date
EP1385723A2 EP1385723A2 (en) 2004-02-04
EP1385723B1 true EP1385723B1 (en) 2009-08-12

Family

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Application Number Title Priority Date Filing Date
EP02745268A Expired - Lifetime EP1385723B1 (en) 2001-04-26 2002-04-26 Electropneumatic control valve with a seal arrangement

Country Status (5)

Country Link
EP (1) EP1385723B1 (en)
AT (1) ATE439284T1 (en)
AU (1) AU2002316881A1 (en)
DE (2) DE10120323C1 (en)
WO (1) WO2002087938A2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012024757A1 (en) 2012-12-19 2014-06-26 Wabco Gmbh Annular sealing element of valve for use in compressed air supply system mounted in e.g. passenger cars, has circumferential sections that include sealing portions respectively located at annular head and annular legs

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20040003736A (en) * 2002-07-04 2004-01-13 주식회사 소프트로닉스 Multi-dimensional signature system
DE102006017503B4 (en) 2006-04-13 2022-12-01 Zf Cv Systems Hannover Gmbh relay valve
DE102006062974B3 (en) 2006-04-13 2023-09-21 Wabco Gmbh relay valve
DE102008012702B4 (en) * 2008-03-05 2013-04-25 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Ventilation device for housing
DE102019119808A1 (en) 2019-07-23 2021-01-28 Wabco Europe Bvba Relay valve for a pneumatic valve unit

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Publication number Priority date Publication date Assignee Title
US4898081A (en) * 1988-08-31 1990-02-06 Allied-Signal Inc. One Piece rear seal for servomotor
DE4202730C1 (en) * 1992-01-31 1993-09-09 Grau Gmbh, 6900 Heidelberg, De Valve with two part metal housing and piston and elastic seal - has injection moulded plastics insert supporting cast running face associated with piston seal.
DE19605562A1 (en) * 1996-02-15 1997-08-21 Bosch Gmbh Robert Pressure regulator for air-operated brakes of commercial vehicle
DE19902225A1 (en) * 1999-01-21 2000-07-27 Knorr Bremse Systeme Trailer control valve for an air brake system of tractor-trailer combinations

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012024757A1 (en) 2012-12-19 2014-06-26 Wabco Gmbh Annular sealing element of valve for use in compressed air supply system mounted in e.g. passenger cars, has circumferential sections that include sealing portions respectively located at annular head and annular legs

Also Published As

Publication number Publication date
WO2002087938A3 (en) 2003-01-09
ATE439284T1 (en) 2009-08-15
DE50213764D1 (en) 2009-09-24
AU2002316881A8 (en) 2006-11-09
EP1385723A2 (en) 2004-02-04
DE10120323C1 (en) 2003-01-16
WO2002087938A2 (en) 2002-11-07
AU2002316881A1 (en) 2002-11-11
WO2002087938A8 (en) 2006-09-14

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